JP2019500264A - Rolling car front wheels - Google Patents

Abstract

The front wheel (8) of the rolling vehicle (4) has two at least one pair of front wheels (10 '') connected to the motion rolling mechanism (20) by each axle journal (60) and two at its two ends. A horizontal steering bar (36) directly connected to the axle journal (60) and hinged to the steering column (86) at an intermediate point, and a recumbent position of the steering bar (36) with respect to a vertical projection plane Releasable means (120) for blocking, and when the releasable means (120) is deactivated, the steering bar (36) is passive to movement of the two vehicles (10 ") When the releasable blocking means (120) is activated, the control bar (36) is prevented from changing its recumbent position, and the recumbent blocking means (120) is activated. Therefore, the relative position between the two axle journals (60) is constrained. [Selection] Figure 1

Description

  The present invention relates to a front wheel (front wheel structure) of a rolling vehicle having a roll block.

  In particular, the automobile according to the present invention can be an automobile including two steering wheels and a rolling wheel at the front portion and an axle driving wheel fixed at the rear portion.

  In the automotive field, there is an increasing supply of “hybrid” vehicles that combine the characteristics of motorcycles in terms of stability and handling of four-wheeled vehicles.

  Such a model is represented, for example, by a three-wheeled vehicle with two front steering wheels and a four-wheeled vehicle known as QUAD.

  More specifically, the above-described three-wheeled vehicle includes two steering wheels and a rolling wheel (that is, tilted or tilted) at the front, and an axle drive wheel fixed at the rear. The rear wheels are intended to provide torque and allow for towing while the paired front wheels are intended to provide vehicle directionality. The paired wheels on the front wheels can be tilted and rolled as well as steered. Thanks to this solution, a car with two wheels on the front wheels can be used in a real car because the vehicle can lean on a curve like a motorcycle, compared to a three-wheeled vehicle with two wheels on the rear wheels. Similar to a motorcycle. However, compared to an automobile with only two wheels, such a vehicle with two pairs of wheels on the front wheels is guaranteed greater stability due to the double support of the front wheels on the ground.

  The front wheels are kinematically connected to each other by a movement mechanism that allows the front wheels to roll in a mirror-like manner, for example by means of an articulated quadrilateral, synchronizing the movement mechanism. Each of the two front wheels of such a vehicle is further provided with two independent suspensions with independent shock absorbers.

  Thus, rolling three-wheeled vehicles are designed to provide the stability and safety of four-wheeled vehicles to the user simultaneously with the handling of two-wheeled vehicles.

This type of rolling three-wheeled vehicle is described in, for example, Patent Document 1 in the name of the same applicant.

  Due to the structural nature of this type of vehicle, the vehicle may fall as a result of accidental and / or uncontrolled rolling movements, for example, at very low speeds or under certain driving conditions such as resting or stopping. there's a possibility that.

  This problem is addressed by equipping the aforementioned vehicle with a roll block system operated by a manual or automatic control system.

  Such a roll block system for automobiles is described in, for example, Patent Document 2 in the name of the same applicant. The roll block system is described in connection with a rolling vehicle with a steering system having an articulated quadrilateral structure and two independent front suspensions. The roll block system is equipped with a mechanical caliper suitable for preventing the movement of the joint quadrilateral so as to prevent the rolling permitted thereby, and the shock to prevent the rolling caused by the asymmetric spring suspension movement of the two wheels. And two hydraulic calipers that are actuated simultaneously by an electric motor acting on a rod arranged in parallel with the absorber.

  The first drawback of the block system described above is its complexity. In practice, three separate blocking devices are required, one acting on the articulated quadrilateral and two acting on the shock absorber.

  This system also has the disadvantage of making the vehicle rigid not only against quadrilateral and / or asymmetric spring suspension movements, but also against rotational movements caused by pitching movements (symmetric spring suspension movements).

  In order to prevent pitching, it is necessary to appropriately set the size of a shock absorber blocking device with an increase in manufacturing cost. In fact, when a vehicle is subjected to an impact from a road where rolling is prevented (eg, from a hole), the prevention system may use an impact peak of the impact force to avoid changes in suspension geometry. You must be able to overcome.

  In some cases, blocking pitching can also affect vehicle behavior and thus safety. For example, if the front wheel is subjected to an impact that overcomes the relative shock absorber blocking force, the wheel will be lifted and thus the car will be lowered on its side. When the collision is over, the blocking device holds the vehicle in the new position reached, thus putting the car in an unsafe state.

  Shock absorber parallel blocking also affects braking. Because the front wheels are blocked lower under the load resulting from the sum of static load and dynamic transmission for braking, the vehicle is actually in a different balance situation than what is required statically. "Blocked".

  Other anti-roll systems for rolling automobiles equipped with a steering system having an articulated quadrilateral structure are described in US Pat. Such anti-roll systems operate directly on the articulated quadrilateral structure and prevent rotation by preventing articulated quadrilateral movement. However, these anti-roll systems cannot suppress rolling motion due to the asymmetric vibration allowed by the two front wheel shock absorbers.

  Furthermore, the anti-roll system described above is specially designed to operate on a steering system having an articulated quadrilateral structure, thus directly linked to the existence of this structure and its mechanical configuration.

  Accordingly, there is a need to develop a rolling vehicle that is adapted to a roll block system that overcomes, in whole or in part, the limitations described above.

  Accordingly, it is an object of the present invention to provide a rolling vehicle front wheel with a roll block system that does not impair the pitching of the vehicle and does not affect maneuvering due to the symmetrical compression of the shock absorber at start-up. It is to eliminate or at least reduce the problems described above with respect to the prior art.

  Another object of the present invention is to make available the front wheels of a rolling vehicle that is adapted to a roll block system that is structurally simple and inexpensive to manufacture the vehicle and fit the vehicle.

  The technical characteristics of the present invention can be clearly understood from the content of the following claims, the advantages of which are made with reference to the accompanying drawings which show one or more embodiments as non-limiting examples. A clearer understanding can be obtained from the following detailed description.

FIG. 1 shows an articulated quadrilateral rolling motion mechanism of a type having a front wheel having a roll block system according to the first embodiment of the present invention and guiding and supporting an axle journal via a rotation-translation type connection system. The perspective view of the motor vehicle provided with is shown.

FIG. 2 is an enlarged detail view of FIG. 1 with respect to the front wheels of the automobile.

FIG. 3 shows an exploded perspective view of the detail of FIG. 2 for the interconnection means between the steering bar and the steering column.

FIG. 4 shows an articulated quadrilateral rolling motion mechanism of the type having a roll block system according to the first embodiment of the present invention and guiding and supporting a wheel axle journal coaxially with the main extension shaft of the upright portion. The rear perspective view of the front wheel of the motor vehicle provided is shown.

FIG. 5 shows an exploded perspective view of the detail of FIG. 4 for the interconnection means between the steering bar and the steering column.

FIG. 6 shows a rolling motion mechanism having an articulated quadrilateral of the type having a roll block system according to a second embodiment of the invention and guiding and supporting an axle journal via a rotation-translation type connection system. It is a front perspective view of the front wheel of a car provided with.

FIG. 7 shows an articulated quadrilateral rolling motion mechanism of a type having a roll block system according to the second embodiment of the present invention and guiding and supporting a wheel axle journal coaxially with the main extension shaft of the upright portion. The rear perspective view of the front wheel of the motor vehicle provided is shown.

FIG. 8 shows some partial details of the front wheel shown in FIGS. 2 and 6 for the interconnection between the axle journal and the articulated quadrilateral. FIG. 9 shows some partial details of the front wheel shown in FIGS. 2 and 6 for the interconnection between the axle journal and the articulated quadrilateral. FIG. 10 shows several partial details of the front wheel shown in FIGS. 2 and 6 for the interconnection between the axle journal and the articulated quadrilateral.

  Referring to the previous figure, reference numeral 4 generally indicates an automobile according to the present invention.

  For the purposes of the present invention, the term automobile includes any motorcycle having at least three wheels, i.e. two aligned wheels and at least one rear wheel, as described better below. It should be pointed out that it should be considered in a broad sense. Thus, such definitions also include so-called quad bikes with two wheels on the front wheels and two wheels on the rear.

  The automobile 4 includes a frame 6 that extends from a front wheel 8 that supports at least two front wheels 10 to a rear portion 12 that supports one or more rear wheels 14. It is possible to distinguish between a left front wheel 10 'and a right front wheel 10' 'whose definition of left and right 10', 10 '' is purely formal and has meaning with respect to the driver of the vehicle. The wheels are arranged on the left and right of the centerline plane MM of the automobile as compared with the observation point of the driver who drives the wheels.

  In the following description and drawings, the front wheels with respect to the centerline plane MM are indicated using quotation marks 'and' to indicate the left and right components of the front wheels, respectively, compared to the observation point of the driver driving it. Refers to the symmetry or specular element.

  For the purposes of the present invention, the automobile frame 6 can be of any shape and size, for example a lattice type, a box type, a cradle, a single or a double. The automobile frame 6 may be an integral type or a plurality of parts. For example, an automobile frame 6 interconnects with a rear frame 13 that can include a vibrating rear fork (not shown) that supports one or more rear drive wheels 14. The aforementioned rear vibrating fork may be connected to the frame 6 by a direct hinge or by lever mechanism and / or intermediate frame intervention.

  According to a general embodiment of the present invention, the front wheel 8 for an automobile has a kinematics on the front wheel frame 16 by means of a front wheel frame 16 and a rolling motion mechanism 20 that allows the front wheels to roll synchronously and mirrorly with each other. And a pair of front wheels 10 ', 10' 'connected together.

  Each wheel 10 ′, 10 ″ is mechanically connected to a wheel rotation pin 68 to support it rotatably about rotation axes R′-R ′, R ″ -R ″. The axle journal 60 is connected to the rolling motion mechanism 20 described above.

  The “axle journal” of a wheel is an automotive vehicle designed to support the rotating pin of the wheel and kinematically interconnect it to the suspension, steering device and the rolling mechanism 20 described above. It is understood that it is a mechanical part. The axle journal has no freedom for the wheel pins and is therefore kinematically integral with it. The axle journal may be formed integrally with the wheel pin or may be mechanically constrained to form a single part.

  The front wheel 8 of the car further comprises:

  Roll block system 100

  Suspension means 90 for providing each axle journal 60 with at least one spring suspension motion relative to the rolling motion mechanism 20.

  The rolling motion mechanism 20 can have any configuration as long as it functions to allow the front wheels to roll synchronously and specularly.

  In particular, such a rolling motion mechanism may be a system configured as an articulated parallelogram system or may be a suspended longitudinal arm system.

The front wheels 8 move the axle journals 60 relative to each other so as to command rotation of the axle journals 60 about the respective steering shafts S′-S ′ and S ″ -S ″ of the front wheels 10 ′, 10 ″. Steering devices 36 and 86 that are connected in a scientific manner.
***

  Preferably, as shown in the accompanying drawings, the aforementioned rolling motion mechanism 20 is an articulated quadrilateral system.

  More particularly, as shown in the example of the accompanying drawings, such an articulated quadrilateral system includes a pair of cross members 24 ′, 24 ″ hinged to the front wheel frame 16 corresponding to the central hinge 28. . The cross members 24 ′ and 24 ″ are connected to each other at the lateral end portions 40 and 44 facing each other by the upright portions 48 ′ and 48 ″ rotated by the lateral end portions 40 and 44 in the side hinge 52. The The cross member 24 and the upstanding portions 48 ′, 48 ″ define the aforementioned joint quadrilateral 20.

  Operatively, each of the upright portions 48 ′, 48 ″ guides and supports one axle journal 60 of the front wheels 10 ′, 10 ″.

  Advantageously, as provided, for example, in the embodiment shown in FIGS. 4 and 7, the articulated quadrilateral rolling motion mechanism 20 includes an upright portion 48 ', 48 ", each of the front wheels 10', 10 The axle journal 60 can be configured to be guided and supported coaxially with the main extension axis TT. In such a case, the suspension means 90 of each front wheel is integrated in a relatively upright state, and a linear spring suspension movement along the main extension axis TT of the upright portions 48 ′, 48 ″ is performed on the axle. Provide to journal 60.

  More specifically, the axle journal 60 includes a sleeve 88 disposed coaxially with the upright portions 48 ′, 48 ″. Between the axle journal 60 and the upright portions 48 ′, 48 ″, suspension means 90 for the wheels 10 are arranged. For example, the suspension means 90 includes a spring and / or a damper.

  In particular, the upstanding portions 48 ′, 48 ″ are hollow so as to at least partially accommodate the suspension means internally. Preferably, the suspension means 90 is arranged coaxially with each upright portion 48 ′, 48 ″.

  Preferably, according to such an embodiment, the coupling between each axle journal 60 and each upright portion 48 ′, 48 ″ is relative to the main extension axis TT of the upright portions 48 ′, 48 ″. The axle journal 60 is of a cylindrical type so as to enable both translation and rotation. Each front wheel 10 ′, 10 ″ has a steering shaft S′-S ′, S ″ -S ″ that coincides with the main extension of the relative upright portions 48 ′, 48 ″ and the symmetry axis TT.

  In particular, each upright portion 48 ', 48' 'extends from the upper end 48s to the lower end 48i. The rotation pin 68 of each front wheel 10 ′, 10 ″ (integrated with the axle journal 60) has a corresponding upright portion 48 ′, 48 ″ of the articulated quadrilateral rolling motion mechanism 20 and an upper end portion 48 s of the 48 ″. It arrange | positions between the lower end parts 48i.

  Alternatively, as provided in the embodiments shown in FIGS. 1, 2 and 6 and FIGS. 8, 9 and 10, the articulated quadrilateral rolling motion mechanism 20 may be a rotational advance type kinematic connection. The system can be configured such that each upright 48 ′, 48 ″ of each front wheel 10 ′, 10 ″ guides and supports the axle journal 60 external to itself.

  More specifically, each axle journal 60 is hinged to the aforementioned joint quadrilateral 20 by a steering hinge 76 disposed corresponding to the upper end portion 48 s and the lower end portion 48 i of each upright portion 48 ′, 48 ″. It is supported by the support bracket 65. The steering hinge 76 defines the respective steering axes S′-S ′, S ″ -S ″ of the wheels 10 ′, 10 ″ parallel to each other.

  More specifically, as specifically shown in FIGS. 2 and 9, the axle journal 60 defines each tilt axis BB that provides a rotational-translational connection between the axle journal 60 and the support bracket 65. It is hinged to the support bracket 65 at the opposite vertical axis ends by at least three inclined hinges 65a, 65b, 65c. Specifically, the axle journal 60 is hinged to the support bracket 65 via the connecting rod 66 by the two hinges 65b and 65c.

  The suspension means 90 for each front wheel may in particular be integrated in each axle journal 60. More specifically, the axle journal 60 includes a sheath into which is inserted a spring (not visible) mechanically connected to the support bracket by a rod. The sheath is movable relative to the rod by the action of a spring.

Operationally, such a system defines a spring suspension movement along a curved track.
***

  According to an embodiment not shown in the accompanying drawings, the aforementioned rolling motion mechanism 20 may be a system having two suspension arms.

More specifically, such a system is hinged to the front wheel frame at its first end, particularly for rotation about a common axis of rotation across the car centerline plane MM. There can be two suspension arms. On its second end, i.e. opposite to the first end, both said arms are suspended by suspension means and then supported by rocker arms and hinged to the front wheel frame. The rotational movement of the two front wheels 10 ′ and 10 ″ is permitted by the vibration of the two suspension arms and the rocker arm. Each suspended arm supports the axle journal 60 of one of the two front wheels 10 'and 10 "at its second end. In particular, each axle journal 60 is rotatably connected to each suspended arm so as to rotate about its own steering shaft S′-S ′, S ″ -S ″. The steering device acts on two gripping parts integral with the axle journal.
***

  In accordance with the present invention, the steering device comprises a steering column 86 and a horizontal steering bar 36 that directly connects two axle journals 60 to each other at their two ends by hinge means.

Preferably, the steering bar 36 extends as a single piece from one end to the other. Alternatively, the bar 36 may be formed from two or more separate portions that are interconnected to form a single body.

  Next, the steering bar moves relative to the steering column 86 about a first rotation axis ZZ that is substantially orthogonal to the rolling plane of the two front wheels 10 ′, 10 ″ defined by the rolling motion mechanism 20. So that the steering column 86 is hinged at an intermediate point between the two ends.

  Advantageously, the interconnection between the steering bar 36 and the steering column 86 is made so that the bar 36 can follow the spring suspension action of the axle journal and front wheels. In other words, the steering bar 36 is supported by the column 86, for example by separating the spring suspension action using a motion mechanism with a double connecting rod.

  The roll block system 100 comprises releasable means 120 for reversibly blocking the recumbent position of the control bar 36 with respect to a vertical projection plane transverse to the car centerline plane MM.

  The “bearing position” of the control bar relative to the vertical projection plane across the car centerline plane MM means the angle formed by the projection of the control bar on the vertical plane.

The vertical projection plane substantially corresponds to a rolling plane. Thus, when the wheel is parallel to the centerline plane, the vertical projection plane is completely perpendicular to the centerline plane MM, or to the centerline plane MM when the wheel is being steered. Tilt.

  In other words, the releasable means 120 for reversibly blocking the recumbent position of the control bar 36 selectively controls the movement of the control bar 36 that corresponds cinematically to the rolling movement of the wheels 10 ′, 10 ″. Can be blocked.

  Operationally, when the aforementioned releasable blocking means 120 are deactivated, the steering bar 36 is free to change its recumbent position relative to the projection plane and interfere with them except to control the steering. Rather, it passively follows the movement of the two wheels 10 ′, 10 ″ relative to each other and to the frame 16.

  When the aforementioned blocking release means 120 is actuated, the control bar 36 is prevented from changing its recumbent position with respect to the aforementioned projection plane, so that the relative position between the two axle journals 60 is reduced. to bound.

  Advantageously, the front wheels 8 and the automobile 4 are equipped with an automatic electronic actuation system.

  The aforementioned means 120 for preventing the recumbent position of the control bar 36 are configured to be controlled by the automatic electronic actuation system according to predetermined control logic, or alternatively or in parallel, they are It is configured to be controlled according to a manual command imposed on the user of the vehicle via a manual actuation system.

Preferably, the front wheels 8 and the vehicle 4 comprise an electronic control system configured to filter manual commands set by the user according to the main operating logic of the vehicle intended to ensure its safety.
***

  As already mentioned at the outset, in the prior art technical solution, the prevention of rolling is done by blocking all elements responsible for rolling, namely the arm, fork, rocker arm and suspension.

  In contrast, according to the present invention, rolling prevention is achieved by interconnecting two front wheels that operate only in two elements, namely the wheel axle journals. For such interconnection, existing components, i.e. the steering bar and the roll block operating on it, are utilized.

  The interconnection of the two wheels in each axle journal makes the roll block system according to the invention selective to rolling motion.

  As described above, the suspension means 90 provides each axle journal with at least a spring suspension motion relative to the rolling motion mechanism 20. Thus, the axle journal is associated with the wheel in a spring suspension motion. For this reason, their interconnection via the roll block system according to the invention (even by activated blocking means) does not interfere with the pitching movement (symmetric spring suspension movement). Thus, the roll block system is transparent to the pitching motion.

  Furthermore, due to the fact that the interconnection between the axle journals 60 is achieved by the steering bar 36, the roll block system 100 according to the invention does not interfere with the steering operation (even if the blocking means are activated). Blocking the recumbent position of the control bar does not impede transmission of motion about the steering axis. Therefore, the roll block system is transparent to steering.

  Thus, from the above, in the activated blocking means, the roll block system 100 according to the invention prevents only rolling movements (derived from asymmetric spring suspension movement) and instead pitches (symmetric spring suspension). In a blocking means that releases and deactivates the steering movement, the roll block system 100 according to the present invention allows the wheel to be steered, rolled (also from an asymmetric spring suspension) and pitched (symmetric spring suspension). It is clear that no kinematic correction for movement is introduced.

Finally, due to the fact that the roll block system 100 acts directly on the axle journal and does not act on the rolling motion mechanism that allows the wheels to rotate synchronously and specularly, the roll block system according to the present invention. 100 does not directly require the presence of the rolling motion mechanism and its mechanical configuration.
***

  Operatively, blocking the recumbent position of the control bar 36 relative to a vertical projection plane across the car centerline plane MM automatically determines the blocking angle α formed by the recumbent surface of at least one wheel relative to the ground. . The steering bar changes its recumbent position with respect to a vertical projection plane transverse to the car centerline plane MM, as long as it is arranged to connect two wheel axle journals at their two ends. Forced to follow the rolling motion of the two wheels. At the moment when the recumbent position of the control bar 36 is forcibly blocked, the aforementioned position also blocks the recumbent position of each wheel, thus corresponding to the change in the angle α formed by the recumbent surface of each wheel with respect to the ground. The rolling motion of the two wheels is prevented.

  Since the two front wheels 10 ′, 10 ″ are kinematically connected together by the rolling motion mechanism 20 so that they rotate synchronously and specularly, the prevention of the wheel angle is also avoided. Brings about the prevention of angles.

  As already mentioned, all this applies regardless of the configuration of the rolling motion mechanism 20 which may be in particular an articulated quadrilateral arm or a suspension arm.

  When the releasable blocking means 120 is deactivated, the control bar 36 can freely change its recumbent position with respect to the projection plane. In other words, when the releasable blocking means 120 is activated. The steering bar 36 is prevented from changing its recumbent position with respect to the projection plane, thereby preventing the rolling movement of two wheels connected thereto via an axle journal.

  Preferably, the aforementioned hinge means, to which the steering bar 36 is connected to the axle journal 60 at both ends, consists of a ball joint or a kinematically equivalent device to the ball joint. In this way, the steering bar 36 can make the second reciprocating movement of the two front wheels 10 ′, 10 ″ relative to the front wheel frame 16 without disturbing or blocking.

  In particular, the aforementioned device, which is kinematically similar to a spherical joint, may be composed of a pair of cylindrical hinges 72, 73 having axes that are orthogonal to each other. Preferably, one of the two hinges 72 of the pair has its own hinge axis that is orthogonal to the rolling surfaces of the two front wheels 10 ', 10' '.

  Preferably, this hinge solution is employed when the steering bar 36 moves in a plane that is substantially parallel to the rolling surfaces of the two front wheels defined by the first rolling motion mechanism 20. This occurs particularly when the rolling motion mechanism is composed of an articulated quadrilateral that guides the motion of the axle journal according to a linear motion.

  “Rolling plane” is understood to mean a plane that crosses the longitudinal direction XX or the direction of movement of the vehicle and is therefore incident on the centerline plane MM of the vehicle. Advantageously, in such a case, of the two hinges of such a pair, the steering bar 36 can move parallel to the aforementioned rolling surface when the releasable blocking means 120 is activated. One of which has its own hinge axis orthogonal to the rolling surfaces of the two front wheels 10 ', 10' '.

  In general, it is preferable that the hinge means of the control bar 36 is composed of a ball joint so as to prevent clogging in the movement of the control bar 36, particularly when the rolling motion mechanism does not allow a straight spring suspension movement with respect to the axle journal.

Advantageously, the ball joint or pair of hinges 72, 73 are connected to the axle journal 60 by a support element 63 integral with the axle journal.

As provided for the embodiment shown in the accompanying drawings, the steering bar 36 connects two axle journals 60 at the same height relative to the ground so that they are parallel to the ground. When the rolling motion mechanism 20 is formed of an articulated quadrilateral, the control bar 36 is particularly substantially parallel to the articulated quadrilateral cross member 28.
***

  In particular, according to the embodiment shown in FIGS. 1 to 7, the releasable means 120 for preventing the recumbent position of the steering bar 36 includes two front wheels 10 ′, 10 ″ defined by the rolling motion mechanism 20. This is suitable for preventing vibration of the steering 36 relative to the steering column 86 about the first rotation axis ZZ, which is substantially orthogonal to the rolling surface of the steering wheel.

  Therefore, the recumbent position of the control bar 36 is prevented in the region where the steering bar 86 is interconnected.

  According to the first embodiment shown in FIGS. 2 and 4 and FIGS. 3 and 5, the releasable blocking means 120 is provided with the steering bar 36 relative to the steering column 86 about the first rotation axis ZZ. It can consist of a band brake 121 associated with the vibration hinge 38. Operationally, the band brake 121, when activated, is suitable for preventing free rotation of the steering bar 36 relative to the steering column 86 about the first axis of rotation ZZ.

  FIG. 2 has a roll block system according to the first embodiment of the invention with an articulated quadrilateral rolling motion mechanism of the type that guides and supports the axle journal of the wheel by means of a rotation-translation connection system. Shows the front wheels of the car.

  More specifically, as shown particularly in FIG. 3, the interconnection area between the steering bar 36 and the steering column 86 is defined by a double hinge. The first hinge 37 has a vertical (or substantially vertical) axis for transmission of rotational movement about the main steering axis YY from the column 86 to the steering bar 36. The second hinge 38 is the vibration described above for the rotation of the control bar 36 about the first rotation axis ZZ that is substantially orthogonal to the rolling surfaces of the two front wheels 10 ′, 10 ″. It is a hinge. In particular, such a first axis ZZ is horizontal or substantially horizontal. The steering bar 36 is provided with a bush 39 at the intermediate position for rotation about the first rotation axis ZZ.

  The band brake 121 is disposed around the first rotation axis ZZ corresponding to the vibration hinge 38. The brake 121 is rotatably associated with the support 123 so as to rotate about the first rotation axis ZZ and extends in a cantilever manner from the bar. And a drum 126 integrally associated with the steering bar 36 via the supporting arm 35. The drum 126 is partially inserted into the support 123 and forms an annular internal space in which the band 122 is accommodated. The two ends 122a and 122b of the band 122 are fixed to the operating lever 125 of the band brake at different positions. By actuating the lever 125, the band 122 is tightened around the drum 126 and prevents its rotation about the hinge axis. This prevents rotation of the control bar 36 about the first rotation axis ZZ that is substantially orthogonal to the rolling surfaces of the two front wheels 10 ′, 10 ″. When the lever 125 is not actuated, the band 122 is not tightened around the drum, and the steering bar 36 is first driven following the rolling movement of the two front wheels 10 ′, 10 ″ and the relative axle journal 60. Freely rotate around the axis ZZ.

  FIG. 4 shows a roll block system according to the first embodiment of the present invention having an articulated quadrilateral rolling motion mechanism of a type that guides and supports the axle journal of the wheel coaxially with the main extension shaft of the upright portion. The front wheel of a car having

  As shown in particular in FIG. 5, the interconnection area between the steering bar 36 and the steering column 86 is defined by a double hinge. This structure is similar to that described in connection with the embodiment in FIG. The first hinge 37 has a vertical (or substantially vertical) axis for transmission of rotational movement about the main steering axis YY from the column 86 to the steering bar 36. The second hinge 38 is the vibration described above for the rotation of the control bar 36 about the first rotation axis ZZ that is substantially orthogonal to the rolling surfaces of the two front wheels 10 ′, 10 ″. It is a hinge. In particular, such a first axis ZZ is horizontal or substantially horizontal. The steering bar 36 is provided with a bush 39 at the intermediate position for rotation about the first rotation axis ZZ.

  The band brake 121 has the same structure and operation as the band brake described with reference to FIG. Also, the components are similar and maintain the same reference in the figure. Therefore, for simplicity, the description of the band brake 121 is not provided with reference to the above.

In place of the band brake 121, a drum brake (not shown in the attached drawings) may be used. Alternatively, other blocking devices or braking devices suitable for this purpose may be provided.
***

  According to the second embodiment shown in FIGS. 6 and 7, the releasable blocking means 120 can be constituted by a caliper 130 acting on the sector 131 of the brake disk. The caliper 130 is integral with the vibration hinge 38 of the steering bar 36 with respect to the steering column 86, and the sector of the disk 131 is integral with the steering bar 36 and around the aforementioned first rotation axis ZZ. It is extended.

  FIG. 6 has a roll block system according to the second embodiment of the present invention with an articulated quadrilateral rolling motion mechanism of the type that guides and supports the axle journal of the wheels by a rotation-translation motion connection system. Shows the front wheels of the car.

  FIG. 7 shows a roll block system according to the second embodiment of the present invention including an articulated quadrilateral rolling motion mechanism of a type that guides and supports the axle journal of the wheel coaxially with the main extension shaft of the upright portion. The front wheel of a car having

According to another embodiment not shown in the accompanying drawings, the releasable blocking means 120 may comprise a ratchet acting on the sprocket. The ratchet 130 is integral with the vibration hinge of the control bar 36 with respect to the steering column 86, and the sprocket is integral with the control bar 36 and concentric with the first rotation axis ZZ.
***

  According to an alternative embodiment not shown in the accompanying drawings, the aforementioned releasable means 120 for preventing the lying position of the steering bar 36 is on a vertical projection plane transverse to the car centerline plane MM. It may be suitable to prevent movement of at least one end of the steering bar 36 in each axle journal 60 so as to prevent the angle formed by the steering bar with said axle journal 60. Therefore, the recumbent position of the steering bar 36 is blocked in the hinge area between the axle journal 60 and the bar 36.

  Said releasable blocking means may be suitable for blocking the movement of the bar only at one end or at both ends.

  Operatively preventing movement of at least one end of the control bar 36 relative to the recumbent surface of each wheel is a recumbent position of the control bar 36 relative to a vertical projection plane transverse to the vehicle centerline plane MM. It means to prevent. As mentioned above, this automatically results in the prevention of the rolling movement of other wheels as well as the wheels that are directly affected by the prevention. Thus, preventing rotation at both ends of the steering bar is not strictly necessary, but serves to ensure a more reliable prevention of the bar.

  The aforementioned releasable means for preventing the recumbent position can be configured in any manner suitable for that purpose.

  Preferably, corresponding to at least one of the two ends, the control bar 36 is connected to each axle journal by hinge means comprising a pair of cylindrical hinges orthogonal to each other. The rotational axes of the pair of first hinges are the rolling surfaces of the two front wheels 10 ', 10' 'so that the steering bar can move parallel to the rolling surface when the blocking means is not activated. Is orthogonal to. The aforementioned releasable means 120 for preventing the recumbent position prevents rotation of the steering bar 36 about the first hinge so as to prevent the angle formed by the axle journal and the steering bar on the plane of rotation. Suitable for doing.

  In particular, the releasable means may comprise a band brake or drum brake arranged at the end of the control bar connected to each axle journal by the pair of cylindrical hinges orthogonal to each other. Operationally, a band brake or drum brake is associated with the first cylindrical hinge to releasably prevent its rotation.

  The control bar 36 may be connected to the axle journal 60 at both ends by a pair of cylindrical hinges orthogonal to each other. The rotation axis of each pair of first hinges is orthogonal to the rolling surfaces of the two front wheels 10 ′, 10 ″. In this case, the releasable means 120 includes a band brake or a drum brake disposed at each end of the control bar 36. Each band brake or drum brake is associated with each first cylindrical hinge of a pair of hinges to prevent its rotation in a releasable manner.

  Alternatively, the aforementioned releasable means may comprise extendable struts to prevent the lying position of the steering bar 36 in the axle journal. The struts are provided with blocking means of that length and connect the control bar 36 diagonally to one of the two axle journals 60. The strut is configured so that the strut does not interfere with the movement of the steering bar 36 relative to the axle journal when the strut remains free in the length direction and when the strut is blocked in the length direction. The steering bar 36 and shaft at both of its two ends via hinge means so that the strut is configured to prevent rotation of the steering bar 36 relative to the axle journal in the common lateral surface of the steering bar and strut. Connect to journal 60.

  The aforementioned releasable means for blocking the recumbent position may comprise two struts that can be extended, each of which comprises a blocking means of its length, which allows the control bar 36 to move out of the two axle journals 60. Connect diagonally to one of the. As in the case of a single strut, in this case too, each of the two struts does not interfere with the movement of the steering bar 36 relative to the axle journal when the strut remains free to extend lengthwise. And so that when the strut is blocked lengthwise, the strut is configured to prevent rotation of the steering bar 36 relative to the axle journal in the common side of the steering bar and strut, Connected to the steering bar 36 and each axle journal at its two ends via hinge means.

Advantageously, the hinge means of each strut consists of a pair of cylindrical hinges having axes orthogonal to each other, one of the two hinges having an axis of rotation orthogonal to the rolling surfaces of the two front wheels.
***

  The invention relates in particular to an automobile 4 having at least one drive wheel and a front wheel 8 according to the invention at the rear, as described above.

If the motor vehicle is a four-wheel drive vehicle, the rear drive wheels 14 in the rear 12 are connected to each other and to the rear frame 13 by the rolling motion mechanism 20 as described above with respect to the front wheels 10, and according to the invention, in particular as described above. Are interconnected to each other by the same roll block system as included in the front wheels of a rolling vehicle having three or four wheels.
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  As described above, the present invention relates to a method for preventing rolling motion of a rolling vehicle having three or four wheels having front wheels according to the present invention. The method comprises the following:

  An activation step of the aforementioned releasable means 120 for reversibly preventing the recumbent position of the control bar 36 so as to prevent rolling movement of the two front wheels; and

  -Deactivation step of the aforementioned releasable means 120 for reversibly preventing the recumbent position of the control bar 36 so as to release the rolling motion of the two front wheels.

The present invention relates to a method for preventing rolling motion of a rolling vehicle having three or four wheels having:

  -Front wheel frame 16,

  At least a pair of front wheels 10 ′, 10 ″, each wheel kinematically connected to each other and to the front wheel frame 16 by means of a rolling motion mechanism 20 which allows the front wheels to rotate synchronously and specularly; 10 ′, 10 ″ are connected to the rolling motion mechanism 20 by each axle journal 60, and the latter supports it rotatably around the rotation axes R′-R ′, R ″ -R ″. Mechanically connected to the wheel rotation pin 68 for

Suspension means 90 for providing each axle journal 60 with at least one spring suspension movement relative to the rolling movement mechanism 20;

  Such methods include: a) Axle journal so as to command rotation of the axle journal 60 about each steering shaft S′-S ′, S ″ -S ″ of each front wheel 10 ′, 10 ″. The operation steps consist of providing steering devices 36, 86 that mechanically connect 60 to each other. The steering device comprises a horizontal steering bar 36 that directly connects two axle journals 60 to each other at their two ends by hinge means. The steering bar 36 is sequentially turned around a first rotation axis ZZ that is substantially orthogonal to the rolling plane of the two front wheels 10 ′ and 10 ″ defined by the rolling motion mechanism 20 described above. Is hinged to the steering column 86 at an intermediate point between its ends.

  The method comprises an operational step b) of providing releasable means 120 for reversibly blocking the recumbent position of the control bar 36 relative to a vertical projection plane transverse to the car centerline plane MM.

  The method further comprises the following two operational steps:

  c) The steering bar 36 is prevented from changing its recumbent position relative to the projection plane so as to limit the relative position between the two axle journals 60 and thus prevent the rolling movement of the two front wheels. Activating the aforementioned releasable means 120 to reversibly prevent the recumbent position of the control bar 36; and

  d) Passive to the movement of the two wheels 10 ′, 10 ″ with respect to each other and with respect to the frame 16 without interfering with them, except to control the steering and thus release the rolling movement of the two front wheels The releasable means 120 is deactivated in order to reversibly prevent the recumbent position of the control bar 36 so that the control bar 36 freely changes its recumbent position with respect to the projection surface so about.

  The invention makes it possible to achieve a number of advantages, as already partially explained.

  The front wheels of a rolling vehicle according to the present invention are equipped with a roll block system that does not prevent either pitching (symmetric spring suspension movement) or vehicle steering during operation. In practice, the roll block system according to the present invention does not introduce any kinematic corrections to the wheel movement due to steering, rolling and spring suspension movements when not activated. When activated, the block system allows for the prevention of rolling motion without interfering with pitching (symmetric spring suspension) and steering motion.

  Furthermore, the front wheel of the rolling vehicle according to the present invention is structurally simple and inexpensive, and includes a roll block system suitable for the vehicle. In practice, it utilizes a control bar that the vehicle already has and that only requires the installation of releasable blocking means in the recumbent position of the control bar.

  The roll block system according to the present invention is also independent of the rolling motion mechanism that allows the wheels to rotate mirror-like in a synchronized manner.

  In addition to being inexpensive, the proposed system also provides pitching (understood as a symmetric suspension movement) for the benefit of structural safety and reduced load by preventing rolling. It is conceptually superior to traditional solutions because it is not blocked.

  Accordingly, the present invention is believed to achieve its intended purpose.

  Apparently, the practical embodiments thereof can take forms and configurations different from those described while remaining within the protection scope of the present invention.

  Moreover, all details may be replaced by technically equivalent elements, and the dimensions, shapes, and materials used may be arbitrary as desired.

Italian Patent Application Publication No. IT2003 MIA001108 Italian Patent Application Publication No. IT2004A000171 European Patent Application No. 2810861 French Patent No. 2953184 European Patent No. 2345576

Claims (22)

Front wheel frame (16),
At least kinematically connected to each other and to the front wheel frame (16) by a motion rolling mechanism (20) that allows the front wheels (10 ', 10'') to roll synchronously and mirrorly. A pair of front wheels (10 ′, 10 ″), each front wheel (10 ′, 10 ″) being connected to the motion rolling mechanism (20) by each axle journal (60), The axle journal (60) is mechanically connected to the wheel rotation pin (68) to rotatably support it (R′-R ′, R ″ -R ″). Front wheels (10 ′, 10 ″),
Suspension means (90) for providing each axle journal (60) with at least one spring suspension motion relative to the motion rolling mechanism (20);
The axle journals (60 ′, 10 ″) are connected to each other so as to command rotation of the axle journal (60) around each steering shaft (S′-S ′, S ″ -S ″). 60) kinematically connecting steering devices (36, 86);
In the front wheel of a rolling vehicle having 3 or 4 wheels comprising a roll block system (100),
The steering device comprises a horizontal steering bar (36) that directly connects the two axle journals (60) to each other at its two ends by hinge means (72, 73), the steering bar (36) being sequentially The steering column (86) around the first rotation axis (Z-Z) substantially orthogonal to the rolling surface of the two front wheels (10 ', 10'') defined by the motion rolling mechanism (20). Is hinged to the steering column (86) at a midpoint between its two ends so as to vibrate against
The roll block system (100) is configured to reversibly block the recumbent position of the steering bar (36) with respect to a vertical projection plane transverse to the vehicle centerline plane (MM) With possible blocking means (120), and when the release blocking means (120) is deactivated, the control bars (36) can interact with each other without interfering with them, except for controlling the steering wheel. By passively following the movement of the two wheels (10 ′, 10 ″) with respect to the frame (16), the recumbent position is freely changed with respect to the projection plane, and the release prevention means (120 ) Is activated, the steering bar (36) is prevented from changing its recumbent position relative to the projection plane, thereby restraining the relative position between the two axle journals (60). Do Front wheel, characterized in that.   The front wheel according to claim 1, wherein the hinge means is constituted by a kinematically equivalent device to a ball joint or ball joint (72, 73).   The device kinematically equivalent to a ball joint is constituted by a pair of cylindrical hinges (72, 73) having axes orthogonal to each other, preferably one of the pair of two hinges (72) is The front wheel according to claim 2, comprising the pair of hinge shafts orthogonal to a rolling surface of the two front wheels (10 ', 10' ').   A wheel according to one or more of the preceding clauses, wherein the steering bar (36) connects two axle journals (60) together at the same height relative to the ground.   The releasable means (120) for preventing the recumbent position of the steering bar (36) is the steering bar (36) relative to the steering column (86) about the first axis of rotation (Z-Z). A front wheel according to one or more of the preceding clauses, suitable for preventing vibrations of the front wheel.   The releasable blocking means (120) is constituted by a band brake (121) or a drum brake associated with a vibration hinge (38) of the control bar (36) with respect to the steering column (86). 121) or the drum brake is suitable for preventing free rotation of the steering bar (36) relative to the steering column (86) about the first axis of rotation (Z-Z) during operation; The front wheel according to claim 5.   The releasable blocking means (120) is constituted by a caliper (130) acting on a brake disk sector (131), and the caliper (130) is connected to the steering column (86) with respect to the steering bar (36). Integrated with a vibrating hinge (38), the disk sector (131) is integrated with the control bar and mounted around the first axis of rotation (Z-Z). Item 6. The front wheel according to item 5.   The releasable blocking means (120) is constituted by a ratchet acting on a gear, and the ratchet is integrated with a vibration hinge of the control bar (36) with respect to the steering column (86), and the gear The front wheel according to claim 5, wherein the front wheel is integrated with the control bar and is concentric with the first rotation axis (Z-Z).   The releasable blocking means (120) blocks the angle formed by the axle journal (60) and the control bar on the vertical projection plane transverse to the vehicle centerline plane (MM). A front wheel according to one or more of the preceding claims, suitable for preventing movement of at least one end of the steering bar (36) on each axle journal (60).   Corresponding to at least one of the two ends, each steering journal (36) is provided by a hinge means constituted by a pair of cylindrical hinges (72, 73) having axes orthogonal to each other. (60) so that when the blocking means is not activated, the control bar (36) can move parallel to the rolling surface of the pair of first hinges (72). A rotating shaft is orthogonal to the rolling surface of the two front wheels (10 ′, 10 ″), and is formed on the rolling surface by the axle journal (60) and the control bar (36). 10. The releasable blocking means (120) is suitable for blocking rotation of the steering bar (36) about the first hinge (72) so as to prevent a tilt angle. front wheel.   The releasable means (120) comprises a band brake or drum brake disposed at the end of the control bar (36) connected to each axle journal by the pair of cylindrical hinges orthogonal to each other. A front wheel according to claim 10, wherein a brake (121) or drum brake is associated with the first cylindrical hinge (72) to releasably prevent its rotation.   The steering bar (36) is connected to the axle journal (60) at both ends by a pair of cylindrical hinges (72, 73) orthogonal to each other, and the rotation shaft of each pair of first hinges (72) is A band in which the two front wheels (10 ′, 10 ″) are orthogonal to the rolling surface, and the releasable means (120) is disposed at each end of the control bar (36). The front wheel according to claim 9, comprising a brake or drum brake, each band brake or drum brake being associated with each first cylindrical hinge (72) to releasably prevent rotation.   The releasable blocking means (120) includes means for blocking its length and an extendable strut that diagonally connects the steering bar (36) to one of the two axle journals (60). The strut is configured not to obstruct the movement of the steering bar (36) relative to the axle journal when the strut remains freely extended in the longitudinal direction, and the strut is blocked in the longitudinal direction. The struts are arranged via hinge means so that the struts are configured to prevent rotation of the steering bar (36) relative to the axle journal in a common lateral surface of the steering bar and struts when Connected to the steering bar (36) and the axle journal (60) at both of its two ends Wheel according to claim 9.   The releasable means (120) each comprises means for blocking its length and is extendable 2 connecting the control bar (36) diagonally to one of the two axle journals (60) The struts are configured so that they do not interfere with the movement of the steering bar (36) relative to the axle journal when the struts remain freely extended in the longitudinal direction, and the struts are long Each strut is configured to prevent rotation of the steering bar (36) relative to the axle journal in the common lateral surface of the steering bar and the strut when blocked in the lateral direction. The steering bar (36) and each axle journal (at each of its two ends by hinge means) Connect to 0), the front wheels according to claim 9.   The hinge means is constituted by a pair of cylindrical hinges (72, 73) having axes orthogonal to each other, and one of the two hinges (72) is in relation to the rolling surface of the two front wheels. 15. A front wheel according to claim 13 or 14, having its axis of rotation orthogonal.   The blocking means (120) in the recumbent position of the steering bar (36) are configured to be controlled by an automatic electronic actuation system according to a predetermined control logic, or alternatively or in parallel they are manually operated A front wheel according to one or more of the preceding clauses, configured to be controlled according to a manual command imposed on a user of the vehicle via an actuation system.   An electronic control system is provided, and the electronic control system is configured to filter manual commands set by the user according to the main operating logic of the vehicle intended to ensure its safety The front wheel according to claim 16.   A car (4) having a drive wheel at the rear and a front wheel (8) according to one or more of the preceding paragraphs.   19. A vehicle (4) according to claim 18, wherein the vehicle (4) comprises two rear drive wheels (14) at the rear (12).   18. Rolling with three or four wheels according to any one of claims 1 to 17, wherein the rear drive wheels (14) in the rear (12) are connected together by a motion rolling mechanism to a rear frame. Car (4) according to claim 19, connected to each other by the same roll block system as included in the front wheels of the car. A method for preventing rolling motion of a motor vehicle having three or four wheels having a front wheel (8) according to any one of the preceding claims,
Activating the releasable means (120) to prevent rolling motion of the two front wheels (10 ′, 10 ″);
Deactivating the releasable means (120) to release the rolling motion of the two front wheels (10 ', 10''). Front wheel frame (16),
At least a pair of kinematically connected to each other and to the front wheel frame (16) by a motion rolling mechanism (20) that allows the front wheels (10 ', 10'') to roll synchronously mirror-like. Front wheels (10 ′, 10 ″), each front wheel (10 ′, 10 ″) being connected to the motion rolling mechanism (20) by each axle journal (60), and rotating shaft (R ′ -R ′, R ″ -R ″) in order to rotatably support it, the axle journal (60) is a front wheel mechanically connected to the wheel rotation pin (68) ( 10 ′, 10 ″),
Method for preventing rolling motion of a rolling vehicle having three or four wheels, with suspension means (90) providing at least one spring suspension motion for said motion rolling mechanism (20) to each axle journal (60) Because
a) The axles to each other so as to command the rotation of the axle journal (60) about each steering shaft (S'-S ', S "-S") of each front wheel (10', 10 ") Providing a steering device (36, 86) for kinematically connecting the journal (60), said steering device connecting the two axle journals (60) to each other at its two ends by means of hinges; A directly connected horizontal steering bar (36) which, in turn, is on the rolling surface of the two front wheels (10 ', 10 ") defined by the motion rolling mechanism (20). The steering column (86) is hinged at an intermediate point between its two ends so as to vibrate relative to the steering column (86) about a first rotation axis (Z-Z) substantially perpendicular to the axis. Rusu And-up,
b) providing releasable means (120) to reversibly prevent the recumbent position of the control bar (36) relative to a vertical projection plane transverse to the vehicle centerline plane (MM);
c) The steering bar (36) restrains its relative position between the two axle journals (60) and thus its recumbent position relative to the projection plane so as to prevent rolling movement of the two front wheels. Activating the releasable means (120) to prevent changing
d) The movement of the two wheels (10 ′, 10 ″) relative to each other and to the frame (16) without interfering with them except that the steering bar (36) controls the steering. Deactivating the releasable means (120) so as to freely change its recumbent position relative to the projection plane so as to passively follow and thus release the rolling motion of the two front wheels. And a method comprising the steps of:

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